Repeating valve shutoff system



Jan. 22, 1946. M CORNELL ET AL Re.. 22,710

REPEATING VALVE SHUTOFF' SYSTEM Original Filed March 7, 1939 8 Sheets-Sheet l y., Wl/m ATTOR N EY Jan. 22, 1946. M. CORNELL ET AL Re. 22,710

REPEATING VALVE SHUTOFF SYSTEM Original Filed March 7, 1939 8 Sheets-Sheet 2 ATTORNEY Jan- 22, 1946. M. CORNELL r-:T A1. Re. 22,710

REPEATING VALVE SHUTO-FF SYSTEM l B Sheets-Sheet 5 Original Filed March 7, 1939 :7, 5i/ Z 7 i. W, g TE VE E l f. E M 6 2 ,l M2/w 4 W.

Jan 22, 1946. M. CORNELL ET Al.. Re. 22,710

l l REPEATING VALVE SHUTOFF' SYSTEM Original Filed March 7, 1959 8 Sheets-Sheet 4 "aa se 276 0 74.-. o I "44 :I 36 70 n 4' I I 54 26 /6 26 50 f4! I 2.0 I

' INVENTOR Jan. 22, 1946. M. CORNELL ET AL L Re, 22,710

l REPEATING VALVE SHUTOFF SYSTEM I Original Filed March '7, 1939 8 Sheets-She'et 5 ZZ/'52. EZ

ATTORNEY Jan. 22, 1946. M. CORNELL ETA; Re. 22,710

-EPEATING VALVE SHUTOFF SYSTEM I Original Filed Marh 7, 1939 8 Sheets-Sheet 6 l I TF5.

.596 .5275 56 @gif-g 37g I T575 422 l?! 420 Ja dof@ 1 Eelnwg@ ATTORNEY JUL 22, 1946- M. CORNELL Erm. Re. 22,710

- REPETING VALVE SHUT-IF SYSTEM u Original Filed March 7, 1939 8 Sheets-Sheet 7 ATTORNEY Jan; 22, 1946. M. CORNELL L-r AL Re. 22,710-

REPEAT ING VALVE SHUTOFF SYSTEM original Filed March v, 19:59 a sheets-sheet 8 INVENTOR Afina (ae/naz 1n/0 ATTORNEY Reuma-um. z2, 194e REPEATING VALVE SHUTOFF SYSTEM Mead Cornell. Cleveland, Ohio. and Alexander R. Whittaker, New York. N. Y., assignora, by mesne assignments, to Pittsburgh Equitable Meter Company, Pittsburgh, Pa., a corporation of Pennsylvania original No. 2.302,529, dated November-i1'. 1942,

Serial No. 260,270, March 7, 1939. Application i for reissue January 29, 1943. Serial No. 473,984

(on. zzz- 14) 23 Claims.

This invention relates to a repeating valve shut-oft' system, especially for rapid measured filling of large containers, for example barrels.

The filling of barrels, for example, the filling of metal barrels with lubricating oil, is difcult.

At the present time, it is the practice to specify the content of the barrel in terms of gallons at a standard temperature, say, 60 F. For this purpose, it is the present practice to actually weigh the contents of the barrel. The barrels are filled through a nozzle having anozzle float or like trip mechanism to shut off the flow of oil when the barrel is lled. 'I'he barrel is weighed before and after filling, and the weight of the contained oil is converted into gallons by reference to suitable conversion tables. The content in gallons is then painted on the side of the barrel. This must be done each time the barrel is illled, for the quantity held by even one lparticulax` barrel may vary from time to time as the barrel is knocked around in service and becomes indented at many points. The barrel illing operation is slow, iirsi; because the iiow through the nozzle is merely gravitational, in orderto permit the desired float shut-oli action, and second because of the time needed to weigh and mark the 'individual barrels.

The primary object of the present invention is to overcome the foregoing difficulties and to provide a valve shut-off system which will permit the barrels to be filled rapidly under-pump pressure. For this purpose, the iiow of oil is measured by a meter, and temperature compensating mechanism is -provided responsive to the temperature of the fluid owing through the meter, so that the measurement will be in gallons at a predetermined standard temperature, say, 60 F. If the particular size of barrel being filled varies from, say, 53 to 54 gallons, due to indentations. etc., a fixed content of 53`gallons, that is, the lower limit, is adopted. Appropriate valve shutoff mechanism stops the delivery of oil at exactly the desired value, say, 53 gallons,'whereupon the apparatus is ready to immediately fill another barrel.

A further object of the present invention is to provide automatic resetting of the trip mech-A anism and quick starting of the valve, it being necessary to merely move a single handle for each barrel lling operation. Still another object is to facilitate changing the gearing' of the trip mechanism so aslto change the trip quantity, as, for example, from 50 gallonsfor one series or size of barrel, to, say, 55 gallons for another series or size of barrel. For this purpose, certain gears are made readily'movable and replaceable. Various gears are provided for diii'erent trip quantities, and to avoid possibility of error or confusion, the gears are preferably inseparably mounted on a large and conspicuously marked gear plate.

Still another object is to employ a positive drive in the temperature compensating mechanism, thereby avoiding the inaccuracy of friction drives which have proved to be notoriously unsatisfactory in practice. A further and ancillary object is to provide means for adjusting the amount .or rate of temperature compensation, thusA making it possible to accommodate differences in the response of different supposedly uniformly manufactured expansion bellows, or diierences in the amount of expansion to be corrected when working with different fluids.

Another object of the invention is to obtain accurate shut-oil, together with high-speed I'llling. The valve mechanism is preferably hydraulically operated, and even the pilot valve may be moved by a spring which is initially tensioned by the starting handle, so that the valve tripping load on the meter is slight, even though the trip mechanism and valve mechanism are made sturdy and rugged for absolute dependability and long life.

Still another object is to provide a manually operable reset means and indicator means for ,the specification and sought to be defined in the 40 claims. ,K The speciiication is accompanied byi drawings, in which:

Fig. l is a partially sectioned side elevation y of an apparatus embodying features of the present invention;

Fig. 2 is a schematic flow diagram for the same; i

Fig. 3 shows the valve tripping mechanism in plan with the cover removed;

Fig. 4 is a section taken in elevation in thev plane of the line 4--4 of Fig. 3;

Fig. 5 is a. section showing a Geneva type gearing between two shafts of the mechanism and is taken in the plane of the line 5-5 of Fig. 4;

Fig. 6 shows the same in frontelevation looking in `the direction of the arrows 6"-6 of Fig. 5;

Fig. 7 is a section explanatory of a cam shifter taken in the plane of the line I-1 of Fig. B;

Fig. 8 is a section `through the cam shifter in operative position, and is taken in the plane of the line 8 8 of Fig. 7;

Fig. 9 is a longitudinal section through the pilot valve or control valve for controlling the hydraulicalh' operated main valve;

Fig. 10 is a transverse section through the rear or pressure controlling part of the control valve of Fig. 9, with the rotor in position to cause closing of the main valve;

Fig. 11 is a transverse section through the forward or bleed controlling part ot the control valve, 'with the rotor in the same position;

Fig. 12 is a transverse section through the rear or pressure controlling part of the control valve (taken in the plane of the line i2-I2 of Fig. 9), with the rotor in position to cause opening o: the main valve;

Fig. 1.3 is a section through the forward or bleed portion of the valve taken in the plane of the line |3-I3 of Fig. 9, with the rotor in the same position;

Fig. 14 is a transverse section through the rear of pressure controlling portion of the control valve, with the rotor in position to cause partial closing of the main valve;

Fig. l5 is a transverse section through the forward or bleed controlling portion with the rotor in the same position;

Fig. 16 is a horizontal fragmentary view showing the manually adjustable elements for the accuracy regulator;

Fig, 17 is a side elevation of the same and is taken in the plane of the line Il-Il of Fig. 3:

Fig. 18 is a section throughv the replaceable paired gears which determine the quantity at which the valve tripping mechanism operates, and is taken in the plane of the line lli-i8 of Fig. 4;

Fig. 19 is a section taken in elevation through the upper or neck portion of the meter and shows the temperature compensating mechanism;

Fig. 20 is a plan view further explanatory of the temperature compensating mechanism and taken `approximately in the plane of the line 29-29 of Fie. 19;

' Fig. 21 is a partially sectioned side elevation of a modification of the aparatus, arranged for single stage shut-ofi, and for manual resetting oi' the trip mechanism if prematurely tripped;

Fig. 22 is a view similar to Fig. 3, :but showing the modified apparatus;

Fig. 23 is a section taken in elevation in the C plane ofthe line 23-23 of Fig. 22;

Fig. 24 is an end elevation of the modified apparatus;

Fig. 25 is a horizontal section through the pilot valve taken approximately on the line 25-25.

of Fig,24;

Fig. 26v is a transverse section through the pilot valve taken on the line 26-26 of Fig. 2,5;

Fig. 27 is a similar section, but with the pilot valve in its valve closing position;

Fig. 28 is a side elevation of the changeable gear mechanism looking in the direction oi the arrows '2B-2B on Fig. 22

Fig. 29 shows the same in plan with the removable gear plate separated from the shafts and fixed gear; l

' Fig. 30 is a horizontal section taken approximately on the line 39-39 of Fig. 21, and showing the temperature compensating mechanism;

Fig. 31 is a section taken in elevation'approximately on the line I I-2i ofFig. 30;

Fig. 32 is a side elevation looking in the direction of the arrows 32-32 of Fig. 31; and

Fig. 33 is a view similar to Fig. 32, but partially sectioned to explain the mounting of the temperature adjusting mechanism.

Referring to the drawings, and more particularly to Figs. l and 2, the apparatus as here exemplified comprises a meter M which may be of conventional type, an hydraulically operated valve V, and valve shut-ofi' mechanism generally designated S. The valve' shut-olf mechanism includes a pilot valve or control .valve C which is connected by suitable piping to control the main valve V. The control valve is initially cocked from valve closing to valve opening position by means of an operating handle H. 'I'he barrel is then rapidly filled with fluid delivered from any suitable tank T under the pressure of a pump P. When the predetermined desired quantity is approached within, say. one gallon, the valve tripping mechanism releases the control valve for movement to an intermediate position causing partial closing'of the main valve V. The rate of flow through the meter is thus slowed down, and when the exact delivery quantity is reached,

the control valve is moved further and produces necessary to preset a register for the desired trip 40 quantity, and in fact no register is needed or provided. The quantity at which the trip action takes place is determined with the aid of replaceable gears indicated at G, and may be still more accurately regulated by means of an accuracy regulator adjusted by means of knob R.

Considering the apparatus in greater detail. the meter M maybe of standard type, it having an inlet I2, an outlet i4, and a neck I6 through which the meter drive passes. compensation is provided, and, for reasons heretofore explained, is extremely valuable for the specific purpose of filling barrels or other containers in which the quantity is to be rated at a standard temperature. The particular temperature compensating mechanism which we prefer to employ is of the type disclosedin co-pending application Serial No. 232,978, entitled Temperature compensated fluid measuring system," iiled October 3, 1938, by Alexander R.. Whittaker, one of the inventors herein. The said mechanism has the advantage of providing a positive drive and a high degree of accuracy, together with minimum frictional load on the meter.

Referring now to Figs. 19 and 20, the meter piston rotates shaft l5, which, through an appropriate train of gearing or so-called intermediate carried in housing 20, drives a shaft I8. The liquid'fllling meter body 22,is confined by packing mechanism 24. Shaft lli drives a shaft 26 through gears 28 and 30. Coaxial with shaft 28 is a driven shaft 32.

The shafts 26 and 32 are coupled together by mechanism which rotates the shafts in unison and which, in addition, superposes -a slight relative movement which causes a slight difference Temperature inthe rotation of shaft 22 relative to shaft 2l. Mechanism of this character is disclosed in United States Patent No. 2,079,197, granted -to Charles P. Bergman on May 4, 1937, and entitled Accuracy regulator. Briey, the shaft 26 turns with it' a frame I4 (Fig. 20) carrying a worm 36, meshing with a worm gear 66 havinga collar 40 which receives driven shaft 32. When 'worm 66 does not rotate on itsl own axis, the shafts 20 and 22 turn in unison as worm 26 revolves about the axis of the shafts. Worm 66 is secured to a ratchet wheel 42 engaged by an operating pawl 44 and a holding pawl 46. Operating pawl 44 is carried by an arm 40 which has an extension I with a rounded or ball-like end received within a groove 62 formed at the inside ofa ring 04. This ring concentrically surrounds shafts 26 and 6.2 and is mounted on horizontal diametrically opposed trunnions 66 carried in stationary bearings 56. With the ring 54 in horizontal position, the shafts rotate in unison, but if the ring is tilted somewhat, it causes an oscillation of the pawl arm 46 during each rotation of shaft 26, and this in turn causes a slight movement of the ratchet wheel and consequently of the worm, which in turn causes a slight movement of`-worm gear 36 so that driven shaft 32 is moved an amount slightly different from the driving shaft 26. This difference in rotation depends on the tilt or angle of ring 54.

The ring is tilted by a temperature responsive element. Specifically, the desired movement is obtained by expansion or contraction of ya liquid carried in a tube or so-called bulb 60 (Fig. 19),

said expansion being manifested in an expansion bellows 62. The tube 6i) is coiled about the upper part of the meter body 22, and its free end 64 is sealed, while the opposite end 66 is connected through member 06 to the expansion bellows 62, the lower end of the bellows being fixedly mounted on member 66 while the upper end is movable and is connected to a vertically reciprocable'post 10 which passes freely through the bifurcated end of an arm 'I2 (Fig. 20) The other end of arm i2 is connected to ring 64 at one of the trunnions. A restoring spring 14 may be provided so that the ring will be tilted in response to contraction as well as expansion of the bellows.

It will be understood that the gear relationshipA in the intermediate 26 and in gears 26 3d is such as te provide a desired roti: on of driven 32 at specined standard temperature, sy', 60 F. When the temperature ci the liquid owing through. the meter body is less than 60 .i the rotation of driven shaft 32 is increased somewhat, while if the temperature is more than 60 F., the rotation of driven shaft 32 is decreased somewhat relative to the desired rotation at the theoretical standard-temperature. The gearing of the temperature compensatingmechanism is housed in an annular housing 16 which is received directly above the neck I6 of the meter, as is clearly shown in Fig. 1.

The. valve tripping or shut-off mechanism S is mounted directly on top of annular housing 16. The casing of the shut-oli mechanism is divided on a line 16, and the entire upper half of the casing may be removed, thus exposing the interior mechanism, as shown in Fig. 3.

Referring now to Figs. 3 and 4, the driven shaft l2 previously referred to leads into the accuracy regulating mechanism R, the output of which is applied to a mitre gear 60. Omitting the accuracy regulator R from consideration for the moment, mitre gear 60 drives mitre gear 02, which in turn rotates a worm 04 meshing with a worm gear 66 therebeneath. Worm gear 06 is mounted on the rear end o! a forwardly extending shaft 66. 'I'he forward end of shaft 66 preferably projects through the front wall 60 of the casing, and carries an -exposed gear 62. This meshes with a gear 64 mounted on ythe forward or outer end of a shaft 96. Shaft 96 carries a mitre gear 66 which meshes with a mitre gear |00 mounted at one end of a shaft |02, which may, for convenience, be called a cam shaft. A second shaft |04 is disposed parallel to cam shaft |02 and is geared to shaft |02 by Geneva type gearing m- .y cluding a driving element |06 on shaft |02 and a driven element |06 on shaft |04. These parts are best shown in Figs. 5 and 6 of the drawings, the driving elementI |06 comprising teeth I I0 adapted to mesh with the eight teeth H2, four of whichl extend axially for locking engagement with the smooth large radius portion I6 of wheel |06. As will be understood by those skilled in the art, the wheel |06 resembles typical transfer pinions used for stepping successive digit wheels in a register. Wheel |06 resembles a typical stepping wheel, except that there are an increased number of teeth A||0. The shaft |04 is intermittently moved in response to continuous rotation of cam shaft |02. Shaft 4|04 carries a pinion ||6 meshing with a gear |20, said gear `being freely rotatable on cam shaft |02., These rotate cooperative parts which come into contact when the meter reachesthe predetermined desired ltrip quantity, and multiples thereof, but which miss one another and do not contact at any different quantity. Specifically, the pinion i6 turns a pin |22 projecting from shaft |04, 'while gear |20 turns cam shifter mechanism including a part |24 which, as will be clear from Fig. 8, is pushed inwardly by pin |22 when gears ||6 and |20 come into proper relationship.

In the specific case here illustrated, the pinion ||6 has eight teeth, and the gear `|20 has twenty teeth. The cooperative parts therefore contact one another after two turns of the gear, or ilve turns of the pinion. By variation of the preceding gearing this is readily made to correspond to the predetermined desired delivery. Obviously, other ratios may be used for pinion HB and gear |20, if desired.

Barrels range in size from 50 to 55 gallons. The mechanism so far described consists essentially oi' a gear train driven bythe meter and having cooperative trip elements |22 and im on two dieren't moving-parts of the gear' train, the gear relationship in the gear train being such that the said trip elements bear against one another when the meter reaches a predetermined desired trip quantity, and multiples thereof, but said elements miss one another at any different quantity. The trip quantity is adjustable by changing some of the gears in the gear train. Specifically, ,the pair of gears 02 and 94 is replaceable, one pair being used for a trip quantity of l50 gallons, another for a trip quantity of 51 gallons, and so on, up to, say 55 gallons in the specific mechanism here illustrated. A much greater range may be provided.

It is important that there beno confusion as tothe trip quantity produced by any particular pair of gears, and it is further important that the gears of the pairs be not mixed up with one another. With this in view, we mount each pair of gears on a plate or gear tag |26. This tag is cie-4 tachably mounted on front wall 88 of the casing by means of a thumb screw |28. Referring now to Fig. 18, it may be explained that gear 82 is fixedly mounted on a hub |30, as by means of brazing, welding, or the like, and that gear 94 is similarly inseparably secured to a hub |22. Hubs |30 and |32 are passed through holes in gear tag |26 before fastening the hubs to the gears, and

the gears are thereafter permanently associated vwith'the gear tag. The gear tag is conspicuously marked with the number of gallons represented by the particular pair of gears in question. Thus, in Fig. 4, the gear tag is marked 52 gals.

The ends of shaft 88 and 96 are preferably split as shown at |34 in Fig. 18. The hubs |30 and |32 are provided with pins extending diametrically therethrough and adapted to be received in the slots |84. To change the trip quantity, it is merely necessary to remove the tag screw l| 28 and to then pry the gears ofi'. the shafts. The assembly of tag and gears is put aside, and another of desired value is applied to the shafts, following which the tag screw |28 is replaced.

The valve tripping impulse, obtained by engagement of pin |22 and the 4part |24 of the cam shifter, is applied only indirectly to the pilot or control valve C. Specifically, the rotor |36 (Fig. 9) of the control valve is coupled at |38 (Fig. 3) to a shaft |40 projecting forwardly through the casing of the trip mechanism. The starting handle H previously referred to is mounted on the forward end of shaft |40, preferably through a lost motion connection provided by slot |42 on the handle, and a pin |44 projecting from the shaft. This is so that the handle can fall back freely to its downward position immediately after starting the mechanism.

The shaft |40 is normally pulled in a counterclockwise direction by. a spiral ribbon spring |46, the inner end of whichis secured to the hub |48 of a notched arm or disk |50, and the outer end |52 of which is anchored on a pin |54 secured to the casing. f

To open the main valve V, the, handle H is turned in a clockwise direction against the resistance of spring |46. It is then held in position by a detent or hook |56 which catches on the tooth |58 of arm |50. Arm |50 is provided with a second notch or tooth |60 which reaches the detent |56 at a position of the rotor corresponding to partial closing of the main valve.

Hook 56 is pivotally mounted on a shaft |62 and is connected thereto by means of a sidewardly projecting finger |64 connected to a cam follower roller |66, disposed over cam shaft |02. Cam shaft |02 carries a cam |68 which is rotatable with but axially slidable on shaft |02. For this purpose, the hub |10 of cam |68 is splined or slidably keyed to shaft |02 by means of a pin |12, as is clearly shown in Fig. 8. Cam |68 is normally moved away from cam follower |66 by means of a compression spring |14, the parts then assuming the relation shown in Figs. 3 and 4. The trip element |24 forms a part of a cam shifter which is pivotally mounted at |18 between spaced arms |18 (Figs. '7 and 8) secured to gear |20. The cam shifter is itself a forked member the branches |80 of which are on opposite sides of cam shaft |02. When the trip elements come into engagement, the shifter |80 is forced against the cam and moves the cam beneath `the cam follower, as shown in Fig. 8.

the run, and cam |88 slides beneath cam foilower |86. The rise of the cam then bears against the cam follower and raises it progressively. At first, the detent |56 frees the ann |50, whereupon the arm oscillates abruptly under the influence of spira1 spring |48 until the second tooth |60 engages detent |58, it being understood that tooth |60 is disposed at a radius greater than tooth |58. The continued rise of' cam |68 further raises the cam follower |88, and with it the detent |56, until the second tooth 60 is also freed, 'this taking place when the exact trip quantity is reached. Spiral spring |48 instantialy oscillates arm |50-, and with it the rotor of the control valve to the shut-oil position, as determined by a motion limiting stop |82.

The reason it is desirable to use an intermit-v tent movement or Geneva type searing between shafts |02 and |04 will now be clear because the action of the trip elements |22 and |24 may be made to precede the nal tripping point, and cam |68 may be slid beneath the cam follower rather quickly. The cam is then kept in operative relation'to the cam follower during its camming action.

In the event of emergency, the control valve may be tripped manually to the shut-off position by pushing a button |84 carrying a pusher rod |86 the inner end of which is disposed adjacent an arm |88 connected to the finger |64 and cam follower |68. Int will be seen, from inspection of Figs. 3 and 4, that 0n pushing button |84 inwardly, the detent |56 is raised, thus freeing the arm |50 for movement to shut-off position.

The mainvalve V and the hydraulic mecha.- nism for operating the same may be described with reference to Fig. l of the drawings. The movable part |90 of the valve, which may, for convenience, be called the valve, is secured to a valve rod |92 connected to a flexible diaphragm |94 clamped between the flanges |96. Diaphragm |94 is reinforced by stiifening plate |98. 'I'he valve is normally urged downwardly to closed position by a compression spring 200. Rod 202 bearing against the stiifening plate and acting as a continuation of the valve rod is formed integrally with a piston ltype valve 204, said valve being vertically slidable in cap 206. Piston 204 is centrally bored at 208 and is provided with a relatively tiny radial bleed opening 2|0, and a substantially larger bleed opening 2|2 located thereabove. Fluid under pressure is supplied above the diaphragm by means 0f a pressure pipe 2|4. Liquid leaving the space above the diaphragm is discharged througha bleed or relief pipe 2|6.

It will be apparent that if liquid is supplied v through pipe 2|4, and is prevented from discharging through pipe 2i6, pressure will be built up above the diaphragm', thus closing the main valve. If, however, pressure line 2|4 is blocked, and relief line 2|'6 is opened, the uid above the diaphragm is discharged, thus permitting the pressure beneath the diaphragm to open the valve.

kto build up and thus causes partial closing of the valve. The valve is not completely closed vbecause when it reaches the desired partially closed position, the large bleed opening 2|2 is exposed and the pressure cannot be further built up. The

cation,

position assumed by the valve is, therefore, determined by the lip 2 I6 en piston valve 204, and ad- Justment may be made on the threaded valve stem with its lock nuts.

The conditions for the pressure line 2|4 and relief line 2|6 are controlled by the control valve C previously referred to. Turning now to Figs. 9 through of the drawings, the rotor |36 is oscillatable within a cylinder 220 which is secured to the casing of the trip mechanism by means` oi' a bolt 222 (Fig. 3). The rotor is inserted in the cylinder from the rear, after which the open end of the valve chamber is closed by a cap 224.

4 a downwardly directed discharge port 236. With the rotor in the positionshown in Fig. 10, the

' ports 2 34 and 238 are aligned, and the iiuid under pressure is supplied to the pressure line 2|4, the latter being connected to the port 236.

The forward portion of valve rotor |36 is cut away, as is indicated at 240 in Fig. ll. The cylinder 220 is provided with inlet and outlet ports 242 and 244, the inlet port 242 being connected to the relief iinezls. The outlet port zu is connected to a pipe 246 (Fig. 1) which is shown as extending back to the discharge side of valve V. .4

The pressure fluid is taken from the inlet side of valve V througha pipe 248 connected to the inlet 230 (Fig. 9) at the rear end of the cylinder. The pressure fluid used to operate the valve flows through the meter and is measuredy by the meter, and is later delivered to the discharge side of valve lV through pipe 246. It will be understood that it is also possible to keep this pressure circuitl outside the meter, that is, pressure iluid may be supplied from a point ahead of the meter so that it is not measured, and may then be bled or returned to the tank. f

Reverting now to Fig. l1, it will be seen that vthe rotor |36 is so disposed as to block the ports v242 and 244, thus eil'ectually preventing discharge ,of liquid from the diaphragm chamber of the,

main valve. The pressure supply line 2|4 being open, and the .bleed line 2|6 being cloned, the main valve is closed.

In Figs. 12 and 13, the valve rotor has been turned clockwise, as is done by the handle H when starting the apparatus. At this time, the `discharge port 236 is blocked, thus preventing supply of pressure fluid to the diaphragm chamber. The bleed ports 242 and 244 are in free communication with one another, thus relieving the pressure in the diaphragm chamber. The main valve is, therefore, moved to its open position.

In Figs. 14 and 15, the rotor has been oscillated in a counterclockwise direction partway back from the open position to the closed position, just as is done when the automatic trip mechanism releases the first tooth of the control 4arm |58, whereupon the detent engagesthe second tooth. At this time, the pressure line issupplied with fluid at a decreased rate because the flow to port 238 takes place through constricted opening 236, The relief passages 242 and 244. are in communithe latter preferably being partially blocked, as shown. but this is not essential because the rate of bleed is more directly determined by the bleed openings in the piston 204 of valve V, as was previously described.A The rotor l position of Figs. 14 and l5, corresponds. of course,

to partial closing of .the main valve.

The apparatus so' far described is further refined by the use of a manually adjustable accuracyl regulator which is interposed between the 1|4 meter and the trip mechanism. This accuracy regulator is preferably of the type disclosed in Bergman Patent No. 2,079,197 previously referred to. Referring to Fig. 3, this regulator is located in the circular part 250 of the casing, near the .16 bottom thereof. It comprises a tiltable ring 252 mounted on .trunnions 254 land operating to oscillate an arm 256 connected to a pawl for intermittently moving a ratchet wheel 258 connected to worm 260 meshing with a worm gear 262. The

zo mechanism is substantially like that previously described in connection with the temperature compensating mechanism, but in the present case, the ring 252 remains fixed in adjustment. Thus, referring to Figs. 16 and 1'1, the ring 252 carries g5 a gear sector 264 meshing with a pinion 266 mounted at the inner end of a shaft 268 carrying a knurled knob '210. Shaft 268 also carriesa pointer 212 cooperating with a scale 214. Pointer 212 is enlarged to provide a locking slot 216 through which passes a locking screw 218 (Fig.

16) the outer end of which is bent to form a handle 280. When handle 280 is turned, the collar .282 thereon clamps the pointer 212 against scale plate 214 and locks the ring in adjusted position.

It is not essential to employ a two stage shutof! for the main valve. In fact, in some cases, as for example, in filling barrels with heavy lubrieating oils at refineries, the two stage shut-ofi may be objectionable, because of the increased do time needed to illl the` barrels. With the two stage shut-oi! considerable time is consumed for the very slow flow preceding shut-off. If the barrels are to be lled, very rapidly, say, one a minute, it may be preferred to use a single stage shut-off. In order to maintain the desired accuracy, the shut-off is made extremely rapid, so that no appreciable error results. Such anarrangement is illustrated-in Figs. 21-2'7 of the drawings to which reference is now made.

In Fig. 21, meter M is followed by hydraulic valve V. The movable part 300 of the valve is controlled by diaphragm 302 loaded by means of compression spring 304. The top of the diaphragm chamber is a simple plate 306, there being no piston valve and no structural parts which might dampen the desired quick action of the valve. Qnly a single pipe 306 leads to the -diaphragm chamber, and when this pipe is vented, the valve is held open by the pressure of the liquidbeneath diaphragm 302, but when pipe 308 is connected to the liquid under pressure, the valve is quickly closed by spring 304. Pipe 3| 0, connected to the inlet side of the valve at.3|2, acts as a pressure line leading to the pilot valve,

05 and pipe 3|4, connected to the discharge lside of the valve at 3| 6, acts -as a vent or relief pipe. All of these connections are preferably made by one-quarter inch piping, in order to help ob tain the desired rapid valve action. (With the two stage shut-off one-eighth inch piping is adequate.)y

Inasmuch as the diaphragm chamber is to be connected to either a pressure lineor a vent line, the control valve or pilot valve C (Fig. 24) may,

in this case, be a simple 'l' valve. Such a valve is shown in Figs. 24 through 27, and referring to these figures, it will be seen that pipe 368 is connected to the control valve at 3I6; that pressure pipe 3I6 is connected to the valve at 326, and that the vent pipe 3I`4 is connected to the control valve at 322.

with an L shaped passage 326. With the rotor in the position shown in Figs. 25 and 26,V the diaphragm chamberis connected to the relief pipe 314, and the main valve V is open. With the control valve turned counter-clockwise through 90 to the position shown in Fig. 27, the diaphragm chamber is connecttd to the pressure pipe, and the main valve V is closed.

The necessary movement of the control valve is obtained by mechanism best shown in Figs. 22 and 23, and much like that previously described, except that the notched arm or disc 336 is provided with only a single notch. It is normally urged counter-clockwise by spring 332 and its movement is limited by suitable pin or stop 334, which, in this case, is mounted on the pin 336 which holds the outer end of spring 332. The starting handle H is similar to that previously described but it need be swung through only a 90 arc at which time the arm 336 is engaged by the hook 338. As before, the hook is lifted to trip the valve by a cam 346 when the latter is moved axially to a position beneath the cam follower 342, The tripping point is so selected as to obtain the desired shut-off. In practice, the release of hook 338 takes place approximately one-eighth of a gallon ahead, and we find that accurate shut-ofi' is obtained despite variations in the temperature of the oil and type of oil. 'I'he barrels are filled very rapidly at a rate of about one a minute.

'I'he modified form of the invention now being described differs from that previously describedl in the gearing of the trip mechanism'. In the present arrangement, the changeable gearing is simplified to provide any desired number of gallons over a wider range, and to insure perfect accuracy throughout the range. Moreover, the

number of teeth on a removable and replaceablel gear may be made to correspond to the number of gallons, thereby eliminating the need for a complex computation. It is also possible to use a totalizer 344 (Figs. 2l and 24).

Referring to Figs. 22 and 23, the drive from the meter is applied to shaft 346 '(Fig. 23). This is connected through mitre gears 348, 356 to a sidewardly extending shaft 352, the latter carrying at its outer end a fixed or non-removable gear 354. This drives aworm shaft 356 through appropriate changeable gears. Worm 358 mounted on shaft 356 meshes with a subjacent worm gear 366 mounted on forwardly extending shaft 362. This, in turn, drivesshaft 364, but the drive is made indirect in order to accommodate the manual reset mechanism which is subsequently described. Specifically, shaft 362 carries a gear 366 which meshes with an idle gear 368, which in turn meshes with a gear 316 carried on shaft 364.

Shaft 364 is geared to cam shaft 312 by means of mitre gears 314, 316. As before, a transfer shaft is provided, this being numbered 316. Transfer shaft 318 carries a transfer pinion 386 which cooperates (as in Fig. 5) with a mutilatedV gear 362 carried on cam shaft 312. In this way the transfer shaft 318 is given intermittent motion. The transfer shaft also carries a pinion 384 meshing with a gear 386 freely rotatable on the cam shaft. Gear 386 carries the cam shifter The rotor 324 is provided 388 while transfer shaft 318 carries a pin 366. As before, when pin 366 and the cam shifter 368 come into coincidence, the cam 346 is moved axially against spring 362 into a position cooperative with cam follower 342. This is preparatory to tripping of the valve, and as cam 346 is rotated by the cam shaft it disengages the hook 338 at the exact desired time.

The changeable gears are best shown in Figs. 28 and 29. Gear 354 is a fixed gear permanently secured to shaft 352. The changeable gears are an idler 364 and a driven gear 366, these being carried on a readily removable gear plate 368. Gear 366 is secured to a hub 466 having a square hole, and the outer or projecting end 462-of shaft 356 is squared to receive the gear. The idler or pinion 364 is freely rotatable on a stud 464 which is riveted to plate 388. Plate 368 is provided lwith a hole 466 which ts freely over shaft .352. It is also provided with a slot 468 which fits over the shank 4I6 of a thumb screw 412. The plate 368 together with idler 364 and driven gear 368 is readily removed by loosening or removing ythe thumb screw. and thereupon moving the plate outwardly oil! the shafts. Another plate with diierent gears may be applied. all of the plates being interchangeable.

In each case the driven gear is so located relative to the hole 466 yas to ilt properly over the square end 462 of shaft 356. 'I'he idler 36:4 is so selected as to mesh with the gears 354 and 365.

The direction of rotation of the shafts is such as tc allow for the interposition of the idler 334. 'I'he advantage of using an idler is that no dimculty arises as'a result of the fixed center to center distance between the shafts 352 and 356. In other words, the gear 366 may be varied greatly in diameter, the difference being taken up by 40 the use of any appropriate sire of idler properly located on the gear plate 366. With only two gears in direct mesh, as in Fig. 4 of the drawings, it sometimes is difficult to simultaneously satisfy the requirement for proper gear ratio and proper center to center spacing while using a whole number of teeth. Slight departures from accuracy may be compensated by adjustment of the microset" or ratio adjustment controlled by .the knob R. This, however, may require trial and error weighing of filled barrels, and also makes it impracticable to use a totalizer, for the reading of the totalizer will become cumulatively wrong if the adjustment at R. is varied for this purpose, instead of being used merely to correct possible inaccuracy in the response of the meter itself.

The removable gear arrangement of Figs. 28

and 29 makes it readily possible to establish exactly the desired gear ratio. Furthermore, the arrangement may be so designed that the number of teeth on the driven gear 366 corresponds numerically to the trip quantity or number of gallons toibe supplied. Thus, in the present case, the gear 366 has 50 teeth for a 50 gallon barrel, 51 teeth for 'a 51 gallon barrel, etc. Ordinarily, the apparatus is supplied .with six gear plates covering a range of from 56 to 55 gallons. However, a much wider range is available, and to fill special requirements the gear 366 may, yfor example, have only 14 teeth, corresponding to theV filling of small 14 gallon barrels.

' The manner in which this result is obtained in the specific mechanism here disclosed, is as follows:

Referring to Figs. 22 and 23, the meter shaft 346 turns one rotation for one gallon of flow (there is, ofcourse, a reduction gear trainbetween the meter piston and shaft 346, this beiner the so-called intermediate".located near the topof the meter body). Shaft 352 also turns one' revolution for one gallon. Fixed gear 354 has40 teeth. Assume driven gear 396 also has 40 teeth, in which case shaft 356 and worm 356 turn one revolution for one gallon. The worm ratio is to 1, and in the specific construction herein shown, the worm is a double worm, while the worm gear 366 has 20 teeth. The gears 366 and 316 are equal. Hence, shaft 264 turns once for 10 gallons, and similarly the cam shaft 312 turns once for 10 gallons. The mutilated or transfer gear 362 has 10 teeth, while transfer pinion 386 has 8 teeth, thus producing one and one-quarter revolutions ofthe transfer shaft for one revolution of the cam shaft. Pinion 364 has 8 teeth and gear 386 has 20 teeth, thus producing a reduction ratio of 2% to 1. The total reduction is, therefore, only l to 2. The reason a simple reduction of 1 to 2 is not` used between pinion 384 and gear 366 is in order to avoid premature tripping or contact between pin 396 and cam shifter 566. For these parts to engage requires two revolutions of the cam shifter, corresponding to five revolutions of the -transfer shaft. This, in turn, requires four revolutions of the cam shaft, and inasmuch as each revolution corresponds to a flow of l0 gallons, the arrangement will trip after a ilow of 40 gallons.

For this result the driven gear 396 on gear plate 398 was provided with 40 teeth. If the driven gear 366 is given an increased number of teeth then the tripping point is reached later, or after a greater ilow. Thus, with 50 teeth the apparatus will trip at 50 gallons, with 51 teeth the apparatus will trip at 51 gallons, etc. 0r, going in the other direction with teeth the apparatus will trip at 15 gallons.

In some cases, the purchaser of the apparatus may require reset mechanism to manually restore the apparatus to zero whenever desired. This is of value, for example, when chaging from one In order to determine the zero position, the

J' cam shaft 212 is provided with. an indicator wheel Y 436, said wheel having a series of arrows and a cross line 432 corresponding to zero. However,

' the indicator wheel 4361s not alone enough, be-

cause the cam shaft turns through four revolutions for the filling of one barrel. Another indicator wheel 434, is, therefore, provided and this wheel is freely rotatable on the cam shaft, but is so geared to the transfer shaft as to turn only one revolution for four revolutions of the cam shaft. The wheel 434 is marked in fractions of a barrel, rather than in gallons, for .the number of gallons'differs in accordance with the 4size of rthe indicator wheel 436 turning four times for one complete revolution of the fraction wheel 434, which is at it should be. The two indicator wheels are exposed through a window 444, as is best shown in Fig. 21. The knob is simply rotated until the fraction wheel reads zero; and the cross line on the other wheel lines up with a suitable l pointer 446 at window 444.

kind of oil to another, for in such case'the meter Referring now to Figs. 22 and 23, knob 426 acts( as a reset knob and is mounted on a shaft 422 which is both rotatable and axially reciprocable. 'I'he shaft is normally urged forwardly by a spring `which may be housed at 424. Shaft 422 carries a large gear 426 which meshes with Ia pinion 426 and carried on shaft 364. The idler gear 366 is freely rotatable on shaft 422, but is axially movable therewith. Knob 426 cannot be rotated unless first pushed inwardly. (If pushed inwardly the idler 366 is disengaged from gear 316, and thereby frees the trip mechanism from the meter and from the totalizer, if a totalizer is used.- Rotation of knob 42D spins the shaft 364 and consequently the trip mechanism. In this way, the trip mechanism may be turned to zero without any accompanying change of the meter and totalizer reading.

In describing the first-form of the invention. reference was madeto the means for automatic temperature adjustment and to the importance of this temperature adjustment, in order that the delivered quantity may be correct at a xed standard temperature, say, 60 F. The present form of the invention is provided vwith similar temperature compensating means, but in the present case there is additionally provided a means for regulating the amount of temperature compensation. Referring to Figs. 30-33 the temperature compensating mechanism is like that previously described in comprising an expansion bellows 450 (Fig. 31). operating on an arm 452 (Fig. 30) connected at 454 to a tiltable ring 456 forming a part of ratio adjusting mechanism of the type previously described. A detail which may be mentioned is the use of two feed pawls 458 and 466 on` the arm which is rocked by ring 456, for by staggering the pawls an amount equal to a half tooth of the ratchet wheel 462, an effect vis obtained equivalent to the use of a ratchet wheel having twice as many teeth.

To provide for adjustment of the amount of temperature compensation, the effective length of the arm 452 is made variable.V For this .purpose, the movable end of the arm is forked as indicated at 464 and the frked end is curved about the vertical or meter shaft 346 as the center. I'he entire ratio adjustment unit is mounted on a. circular plate 466, and this plate is received above flange 466 and below flange 410 (Fig. 33). Flangellll is cut away at 412 (Fig. 30) to provide clearance at each side of the upright post or bearings 414 of the ratio adjusting unit. This provides room for oscillation of thcl complete unit, and it will be evident from inspection of Fig. 30 that inasmuch as the bellows 450 is stationary, the oscillation of the unit may be used to length or shorten the effective length of arm 452. The adjustment may be made from the outside by means of a knob 416 carried at the stationary scale 484 as is best shown in Fig. 32.

The resulting adjustment of the amount of temperature compensation is desirable, because of non-uniformity in the manufacture of the bellows, and also because different liquids may A have diii'erent expansions or temperature coeilicients.

It is lbelieved that the construction and operation of our improved repeating valve shut-off system. as well as the many advantages thereof,

`will be apparent from the foregoing detailed description thereof. The main valve V isv normally closed, regardless of whether the pump is operated, :because the valve is closed both gravitationally and by the spring.

To fill barrels, it is merely necessary to start the pump, to insert the nozzle of the discharge pipe in the first barrel, and to then swing the starting handle H. This moves the pilot valve to the starting position, and the main valve is promptly opened by the relief of pressure above the diaphragm. The meter turns the cam shaft and this intermittently turns the pinion or transfer shaft. When the delivery is 'nearly completed, the cooperative trip elements come into contact, as shown in Fig. 8, thus shifting the cam beneaththe cam follower. The cam then moves detent or hook upwardly, releasing the arm and permitting spiral spring to shift the f control valve rotor from the starting position. With two stage shut-off the main valve is partially closed and later the detent again releases the rotor with consequent complete closing of the main valve. With single stage shut-off the main valve is completely closed immediately.

To iill another barrel the nozzle is simply inserted in the next barrel and the starting handle again moved. When the second barrel is filled, the nozzle is transferred to a third barrel. l

etc. For each barrel it is merely necessary to move the starting handle, and all of the barrels are filled with the same amount of liquid. Should some emergency make it desirable to prematurely trip the main valve, it is merely necessary to push the button |84. The amount delivered to the barrels is corrected for desired Astandard temperature by the automatic temperature compensating mechanism.

If the barrel size is changed, it is merely necessary to change the replaceable gears, as was previously described. Occasionally, a filled barrel may be weighed to check the accuracy of the apparatus. If an error is found, due to the response of the meter itself, such error may be corrected by the ratio adjusting mechanism under control of the knob R. If the error is caused by incorrect temperautre compensation, this factor may be varied by the mechanism shown in Figs. 30-33.

It is believed that the construction and operation. as wel1 as the many advantages of our improved repeating valve shut-off system, will be apparent from the foregoing detailed description. It will also be apparent that while we have shown and described our invention to preferred formsr many changes and modications may be made in the structures disclosed without departing from the spirit of the invention defined in the following claims.

We claim:

1. A repeating trip mechanism for measuring purposes, said mechanism comprising a gear train including meshing spur gears, a radially projecting trip element rotatable with one of said meshing spur gears, a radially projecting trip element rotatable with the other of said meshing 5 spur gears, and cooperative trip elements on two tionship or ratio in said gear train being such that said trip elements bear radially against one another -when the measurement reaches a predetermined desired trip quantity and each multiple thereof, but said trip elementsescape one another at any dierent quantity.

l 2. A repeating valve shut-oil' system comprising a meter, a gear train driven thereby. cooperative trip elements on two different parts of said gear train, the gear relationship in said gear train -being such that said trip elements vbear against one another when the meter reaches a predetermined desired trip quantity and each multiple thereof, but said trip elements escape one another at any different quantity, and temperature responsive means to compensate for variations in temperature of the fluid passing through the meter.

purposes. said mechanism comprising a gear train having4 a plurality of gears arranged in series,

f the earlier gear acting as an input or driving section, and the later gear acting as a trip section,

3o cooperative trip elements on two different rotating parts of the trip section of said gear train,

the gear relationship in said gear train being such that said trip elements bear against one another when the measurement reaches a predetermined desired trip quantity and multiples thereof, .but

said trip elements escape one another at any different quantity, an readily replaceable gears in the driving section of said 'gear train for determining the aforesaid desired trip quantity.

4. A repeating valve shut-off system comprising a meter, a driven gear train, a'driving gear train between the meter and the driven gear train, cooperative trip elements on two diii'erent parts of said driven gear train, said trip elements bearing against one another when the meter reaches a predetermined trip quantity and multiples thereof, but said trip elements missing one another at any different quantity, readily replaceable gears in said driving gear train for determining the desired trip quantity, and temperature responsive means to compensate for variations in the temperatureof ,the fluid passing through the meter.`

5. Repeating shut-oil mechanism for use with a valve and a measuring means, said mechanism comprising a. cam shaft, a cam rotatable with said shaft, a cam follower for causing tripping of a valve, means normally separating the cam and cam follower, a gear train means whereby a measuring means may be iused for driving the gear train and the cam shaft, cooperative trip elements on two diiferent parts of said gear train, the gear relationship in said gear train being such that said trip elements bear against one another 55 and function to shift the cam and cam follower into operative position when the measurement approaches a predetermined desired quantity and multiples thereof, but said elements missing one another at any diiferent quantity, some of the gears in the aforesaid gear train being replaceable to determine the desired trip quantity.

6. Repeating valve shut-off mechanism comprising a valve, a cam shaft arranged to be driven by a meter. a cam rotatable with said shaft, a

cam follower for causing tripping of the valve.

different parts of said gear train, the gear rela- 3. A repeating trip mechanism for measuringv tive position when the meter approaches a predetermined desired quantity and multiples thereof, but said elements missing one another at any different quantity, some of the gears in the aforesaid gear train being replaceable to determine the desired trip quantity, and automatic temperature compensating means between the meter and the cam shaft for compensating for changes inv the temperature of the fluid passing through the meter.

7. Repeating valve shut-olf mechanism comprising a valve, a cam shaft arranged to be driven by a meter, a cam rotatable with said shaft, a cam follower for causing tripping of the-valve, means normally separating the cam and cam follower, a gear train also arranged to be driven by said meter, cooperative trip elements on two different parts of said gear train, the gear relationship in saidgear train being such ythat said trip elements bear against one another and function to shift the cam and cam follower into operative position when the meter approaches a predetermined desired quantity and multiples thereof, but said elements missing one another at any different quantity, some of the gears in the aforesaid gear train being changeable to determine the deative position when the meter approaches apresiredtrip quantity, and temperature compensating means including'a worm and related gearing for locking together two shafts between the meter and the cam shaft, pawl and ratchet mechanism for intermittently rotating thev worm a slight amount, an oscillating member connected to the pawl for oscillating the pawl during each revolution of the shafts, adjustment means to vary the amount of oscillation of the oscillatable member,

and. a liquid lled bulb immersed in the fluid in the meter and connected to an expansion bellows having one end fixed and the other end movable and connected to the adjustment means.

8. Repeating shut-off mechanism for use with a valve and a measuring means, said mechanism comprising a control arm having positions corresponding to open and closed positions of a valve, means urging the arm to the latter position, detent means for holding the arm in the rst position, a cam shaft, a cam rotatable with said shaft,

a cam follower connected to the aforesaid detent means for releasing the same, means normally separating the cam and cam follower, a gear train means whereby a measuring means may be used for driving the gear train'and the cam shaft,

cooperative trip elements on two different parts of said gear train. the gear relationship in said gear train being such that said trip elements bear against one another and function to shift the cam and camI follower into operative position when the measurement approaches a predetermineddesired quantity and multiples thereof, but

said elements missing one another at any diiferent quantity, some of the gears in the aforesaid gear train being changeable to determine the desired trip quantity. e 9.A Repeating valve shut-olf mechainsm com prising an hydraulically operated main valve, a control valve therefor including a rotor having positions corresponding to open and closed positions of the main valve, means urging the rotor determined desired quantity and multiples thereof, but said elements miss 'one another at any different quantity, some of the gears in the aforesaid gear train being changeable to deter- I mine the desired trip quantity.

10. Repeating .valve shut-off mechanism comprising an hydraulically operated main valve, a control valve therefor including a rotor having positions corresponding to open and closed positions of the main valve, means urging the rotor to the latter position, detent means for holding the rotor in the iirst position, a cam shaft arranged to be driven by a meter, a cam rotatable with said shaft, a cam` follower connected to the aforesaid detent means for releasing tse same, means normally separating the cam and cam follower, a gear train also arranged to be driven by said meter, cooperative trip elements on two different parts of said gear train, the gear rela' tionship in said gear train being such that said trip elements bear aaginst on another and func-l tion to shift the cam and cam follower into operdesired trip quantity, andI automatic temperaturecompensating means between the meter and the cam shaft for compensating for changes in the temperature of the fluid passing through the meter.

11. Repeating valve shut-olf mechanism comprising a meter, a cam shaft, a gear train leading from said meter to said cam shaft, a-cam rotatable with and axially slidable on said cam shaft, a cam follower for operatively controlling the valve, a spring normally moving the cam away from the cam follower, a pinion driven from said gear train, a gear meshing with said pinion, a. cam shifter rotatable with said. gear, means on said pinion cooperating with said cam shifter to shift the cam into operative position when the meter reaches a predetermined trip quantity and successive multiples thereof, the teeth of the gearing being such that the aforesaid means do not come into operative relation at any different quantity, and automatic temperature compensating mechanism between said meter and said cam shaft for compensatingfor changes in the temperature of the fluid passing through the meter. A l

l2. Repeating shut-olf mechanism for use with a valve, said mechanism comprising a cam shaft,

l a gear train leading to said cam shaft, a. cam

to thelatterposition, detent means for holding rotatable with and axially slidable on said cam shaft, a cam follower for operatively controlling a valve, a spring normally moving the cam away from the cam follower, a pinion driven from said gear train, a gearmeshing with said pinion, a camvshifter rotatable with said gear, means on said pinion cooperating with said cam shifter to shift the cam into operative position when the gear train reaches a predetermined trip quantity and successive multiples thereof, the teeth of the pinion and gear` being such that the aforesaid means do not come into operative relation at any different quantity, anda pair of gears in the aforesaid gear train leading to the cam shaft being replaceable to determine the desired trip quantity.

- cam to a position away from the camfollower,

a pinion onsaid second shaft, a gear freely rotatable on the cam shaft, a cam shifter rotatable with said gear, means on said second shaft cooperating with said cam' shifter to shift the cam into operative position when the gear train reaches a predetermined trip quantity and successive multiples thereof, the teeth of the gearing being such that the aforesaid means do not come into operative relation at any different quantity, a pair of gears in the aforesaid gear train leading to the cam shaft being replaceable to determine the desired trip quantity.

14. A repeating shut-off mechanism for use with a valve, said mechanism comprising a trip mechanism, a driving gear train leading to the trip mechanism, said 'trip mechanism functioning to trip a valve when the driven gear train reaches a predetermined trip quantity and multiples thereof, but not at any different quantity, said driving gear train including spaced shafts, a gear fixed on one of said shafts, and a readily removable and replaceable gear plate associated with said shafts and carrying a gear adapted to oe received on the other shaft and carrying an idler pinion for driving said gear and so dimensioned and disposed on the plate as to meshf'with the fixed gear when the plate-carried gear is in its shaft, the gear ratios in the gear trains being such that the number of teeth on th'e platecarried gear corresponds numerically to the desired trip quantity.

15. A repeating shut-off mechanism for use with a valve, said mechanism comprising a driven gear train, a driving gear train leading to the driven'gear train, cooperative trip elements on two different parts of said dn'ven gear train, said trip elements bearing against one another when the driven gear train reaches a predetermined trip quantity and multiples thereof, but said trip elements missing one another at any different quantity, said driving gear train including spaced shafts, a gear fixed on one of said shafts, and a readily removable and replaceable gear plate associated with said shafts and carrying a gear adapted to be received on the/other shaft and carrying an idler pinion for driving said gear and so dimensioned and disposed on the plate as to mesh with the fixed gear when the platecarried gear is on its shaft, the gear ratios in the gear trains being such that the number of teeth on the plate-carried gear corresponds numerically to the desired trip quantity.

16.' A repeating valve shut-oifsystem comprising a meter, a driven gear train, a driving gear train between the meter and the driven gear train, cooperative trip elements on two different parts of said driven gear train, said trip elements bearing against one another when` Athe meter reaches a predetermined trip quantity and multiples thereof, but said trip elements missing one other shaft and carrying an idler pinion for driving said gear and so dimensioned and disposed on the plate as to mesh with the fixed gearwhen the plate-carried gear is on its shaft, the

' gear ratlos in the gear trains being such that the number of teeth on the plate-carried gear corresponds numerically to the desired trip quantity, and temperature responsive means to compensate for variations in the temperature of the uid passing through the meter.

17. A repeating trip mechanism, said mechanism comprising a driven gear train, a driving gear train leading to the driven gear train, cooperative trip elements on two different parts of said driven gear train, said trip elements bearing against one another when the driven gear train reaches a predetermined trip quantity -and multiples thereof, but said trip elements missing one another at any different quantity, readily removable and replaceable gears for determining the desired trip quantity, re-set means including means to disengage a part of the driving gear train in order not to affect any Imeans ahead of the gear train during re-setting of the trip mechanism to zero, and indicator wheels associated with said driven gear train for indicating when the trip mechanism has been re-set to zero.

18. A repeatingtrip mechanism, said mechanism comprising a driven gear train, a driving gear train leading to the driven gearv train, cooperative trip elements on two different parts of said driven gear train, said trip elements bearing against one another when the driven gear train reaches a predetermined trip quantity and multiples thereof, but said trip elements missing 'one another at any different quantity, said driving gear train including spaced shafts, a gear fixed on one of said shafts, a readily removable and replaceable gear plate associated with said shafts and can'ying a gear adapted to be received in the other shaft and carrying an idler pinion meshing with said gear and so dimensioned and disposed on the plate as to drive the fixed gear when the plate-carried gear is on its shaft, the 'gear ratios in the gear trains being such that the number of teeth on the plate-carried gear corresponds numerically to the desired trip quantity, re-set means including means to disengage a, part of the driving gear train in order not to affect any means ahead of the gear train during re-setting of the trip mechanism to zero, and indicator wheels associated with said driven gear train for indicating when the trip mechanism has been re-set to zero.

19. A repeating valve shut-off system comprisy temperature responsive means.

20. A repeating valve shut-off system compris- Ilng a meter, a driven gear train, a driving gear train between the meter and the driven gear train, cooperative trip elements on two different' parts ot said `driven gear train, said trip elements bearing against one another when the meter reaches a predetermined trip quantity and multiples thereof, but said trip elements missing one another at any different quantity, readily replaceable gears in said driving gear train for determining the desired trip quantity, temperature responsive means to compensate for variations in the temperature of the fluid passing through the meter, and manuaiLv adjustable means-incliidinirA a scale and pointer for adjusting the amount of temperature compensation produced by the temperature responsive means.

21. A repeating valve shut-oil system compris ing a meter, a gear train driven thereby, cooperative trip elements on two different parts of said gear train, the gear relationship in said gear train being such that said trip elements bear against one another when the meter reaches a predeter- 1 1 member, and a squid-nues' hun immersed .xn the iiuid in the meter and connected to an expansion bellows having one end nxed and the other end movable and connected to the adjustment means.

22. A repeating valve shut of! system comprising a fluid meter, a valve in the flow line oi' the meter, predetermining means operated by the meter to close said valve when a predetermined quantity of fluid ows through said meterI temperature responsive means acting between the meter and predetermining means to compensate for variations in the temperature oi' the iiuid passing through the meter, and manually adjustable means fox-.adjusting the amount of temperature compensation produced by the, temperature responsive means.

23. A repeating valve ing a uid meter,a predetermining register means operated by the meter to shut oi! the ilow of iiuid when a predetermined quantity oi' fluid\ iiows through the meter, speed change mechanism connected to be continually driven by said meter and connected to continuallyv drive said predeterminins register means, temperature responsive means for adjusting said speed change ymechanism to compensate for variations in the temperature of the iluid passing through the meter, and manually adjustable means for adjusting the amount of -temperature ycompensation in accordance with the an coemcient of expansion of said nuid.

` l #MEAD CORNELL, ALEXANDER R. WHI'ITAKER.

shut oi system compris.- 

